EP3232064B1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
EP3232064B1
EP3232064B1 EP17166030.1A EP17166030A EP3232064B1 EP 3232064 B1 EP3232064 B1 EP 3232064B1 EP 17166030 A EP17166030 A EP 17166030A EP 3232064 B1 EP3232064 B1 EP 3232064B1
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EP
European Patent Office
Prior art keywords
vane
cylinder
piston
chamber
concave portion
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Active
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EP17166030.1A
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German (de)
English (en)
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EP3232064A1 (fr
Inventor
Akira Inoue
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Fujitsu General Ltd
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Fujitsu General Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/332—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00

Definitions

  • the present invention relates to a rotary compressor.
  • an annular piston provided to be eccentric to a rotation shaft rotates in a cylinder, a tip end of a plate-like vane which reciprocates in the cylinder in accordance with rotation of the piston is thrust to an outer circumferential surface of the piston, and accordingly, the inside of the cylinder is divided into a compression chamber and an inlet chamber.
  • the vane slides in a vane groove of the cylinder nipped by an end plate and an intermediate partition plate in a state of being biased by a spring.
  • WO 2014/025025 is an example of the related art.
  • an object of the invention is to provide a rotary compressor which can suppress a partially contact state of the vane with the piston, and improve operation reliability of the vane.
  • a rotary compressor including: a sealed vertically-placed cylindrical compressor housing in which a discharging unit for a refrigerant is provided in an upper portion, and an inlet unit for the refrigerant is provided in a lower portion; a compressing unit which is disposed in the lower portion of the inside of the compressor housing, and which compresses the refrigerant suctioned from the inlet unit, and which discharges the refrigerant from the discharging unit; and a motor which is disposed in the upper portion of the inside of the compressor housing, and which drives the compressing unit, in which the compressing unit includes annular upper and lower cylinders, an upper end plate which closes an upper side of the upper cylinder, a lower end plate which closes a lower side of the lower cylinder, an intermediate partition plate which is disposed between the upper cylinder and the lower cylinder, and which closes the lower side of the upper cylinder and the upper side of the lower cylinder, a rotation shaft which is supported by
  • Fig. 1 is a longitudinal sectional view illustrating a rotary compressor according to an embodiment.
  • Fig. 2 is an exploded perspective view illustrating a compressing unit of the rotary compressor according to the embodiment.
  • Fig. 3 is a lateral sectional view when the compressing unit of the rotary compressor according to the embodiment is viewed from above.
  • a rotary compressor 1 includes: a compressing unit 12 which is disposed in a lower portion of the inside of a sealed vertically-placed cylindrical compressor housing 10; a motor 11 which is disposed on an upper portion of the inside of the compressor housing 10, and drives the compressing unit 12 via a rotation shaft 15; and a vertically-placed cylindrical accumulator 25 which is fixed to an outer circumferential surface of the compressor housing 10.
  • the accumulator 25 is connected to an upper cylinder chamber 130T (refer to Fig. 2 ) of an upper cylinder 121T via an inlet unit configured of an upper inlet pipe 105 and an accumulator upper L-pipe 31T, and is connected to a lower cylinder chamber 130S (refer to Fig. 2 ) of a lower cylinder 121S via an inlet unit configured of a lower inlet pipe 104 and an accumulator lower L-pipe 31S.
  • the motor 11 includes a stator 111 which is disposed on an outer side, and a rotor 112 which is disposed on an inner side.
  • the stator 111 is fixed to an inner circumferential surface of the compressor housing 10 in a shrink fit state
  • the rotor 112 is fixed to the rotation shaft 15 in a shrink fit state.
  • a sub-shaft unit 151 on a lower side of a lower eccentric portion 152S is supported to be freely rotated by a sub-bearing unit 161S provided in a lower end plate 160S, and a main shaft unit 153 on an upper side of an upper eccentric portion 152T is supported to be freely rotated by a main bearing unit 161T provided in an upper end plate 160T.
  • the rotation shaft 15 is supported to be freely rotated with respect to the compressing unit 12 as each of an upper piston 125T and a lower piston 125S is supported by the upper eccentric portion 152T and the lower eccentric portion 152S which are provided by applying a phase difference of 180 degrees therebetween.
  • the upper piston 125T and the lower piston 125S are operated to revolve along the inner circumferential surfaces of each of the upper cylinder 121T and the lower cylinder 121S.
  • lubricant oil 18 having an amount by which the compressing unit 12 is substantially immersed is sealed on the inside of the compressor housing 10.
  • An attachment leg 310 (refer to Fig. 1 ) which locks a plurality of elastic supporting members (not illustrated) that support the entire rotary compressor 1 is fixed to a lower side of the compressor housing 10.
  • the compressing unit 12 compresses a refrigerant suctioned from the upper inlet pipe 105 and the lower inlet pipe 104, and discharges the refrigerant from a discharge pipe 107 which will be described later.
  • the compressing unit 12 is configured by stacking an upper end plate cover 170T including a bulging portion in which a hollow space is formed in an inner portion, the upper end plate 160T, the annular upper cylinder 121T, an intermediate partition plate 140, the annular lower cylinder 121S, the lower end plate 160S, and a flat plate-like lower end plate cover 170S, in order from above.
  • the entire compressing unit 12 is fixed by a plurality of penetrating bolts 174 and 175 and an auxiliary bolt 176 which are disposed on a substantially concentric circle from above and below.
  • an upper cylinder inner wall 123T is formed along the circle concentric to the rotation shaft 15 of the motor 11.
  • the upper piston 125T which has an outer diameter smaller than an inner diameter of the upper cylinder 121T is disposed, and between the upper cylinder inner wall 123T and the upper piston 125T, the upper compression chamber 133T which suctions, compresses, and discharges the refrigerant is formed.
  • the lower cylinder 121S along the circle concentric to the rotation shaft 15 of the motor 11, a lower cylinder inner wall 123S is formed.
  • the lower piston 125S which has an outer diameter smaller than an inner diameter of the lower cylinder 121S is disposed, and between the lower cylinder inner wall 123S and the lower piston 125S, the lower compression chamber 133S which suctions, compresses, and discharges the refrigerant is formed.
  • the upper cylinder 121T has an upper side protruding portion 122T which is overhung from a round outer circumference.
  • an upper vane groove 128T which extends from the upper cylinder chamber 130T to the outside in a radial shape, is provided.
  • an upper vane 127T is disposed to be slidable.
  • the lower cylinder 121S has a lower side protruding portion 122S which is overhung from the round outer circumference.
  • a lower vane groove 128S which extends from the lower cylinder chamber 130S to the outside in a radial shape, is provided.
  • a lower vane 127S is disposed to be slidable.
  • an upper spring hole 124T is provided at a depth which does not reach the upper cylinder chamber 130T.
  • An upper spring 126T is disposed in the upper spring hole 124T.
  • a lower spring hole 124S is provided at a depth which does not reach the lower cylinder chamber 130S.
  • a lower spring 126S is disposed in the lower spring hole 124S.
  • a lower pressure guiding-in path 129S which communicates with the outer side in the radial direction of the lower vane groove 128S and the inside of the compressor housing 10, has an opening portion that introduces the compressed refrigerant on the inside of the compressor housing 10, and applies a back pressure to the lower vane 127S by a pressure of the refrigerant, is formed.
  • the refrigerant compressed on the inside of the compressor housing 10 is also introduced from the lower spring hole 124S.
  • an upper pressure guiding-in path 129T which communicates with the outer side in the radial direction of the upper vane groove 128T and the inside of the compressor housing 10, has an opening portion that introduces the compressed refrigerant on the inside of the compressor housing 10, and applies a back pressure to the upper vane 127T by a pressure of the refrigerant, is formed.
  • the refrigerant compressed on the inside of the compressor housing 10 is also introduced from the upper spring hole 124T.
  • an upper inlet hole 135T which is fitted to the upper inlet pipe 105 is provided in the upper side protruding portion 122T of the upper cylinder 121T.
  • a lower inlet hole 135S which is fitted to the lower inlet pipe 104 is provided in the lower side protruding portion 122S of the lower cylinder 121S.
  • upper and lower parts of the upper cylinder chamber 130T are closed by each of the upper end plate 160T and the intermediate partition plate 140.
  • Upper and lower parts of the lower cylinder chamber 130S is closed by each of the intermediate partition plate 140 and the lower end plate 160S.
  • the upper cylinder chamber 130T is divided into an upper inlet chamber 131T which communicates with the upper inlet hole 135T, and the upper compression chamber 133T which communicates with an upper discharge hole 190T provided in the upper end plate 160T.
  • the lower cylinder chamber 130S is divided into a lower inlet chamber 131S which communicates with the lower inlet hole 135S, and the lower compression chamber 133S which communicates with a lower discharge hole 190S provided in the lower end plate 160S.
  • the upper discharge hole 190T which penetrates the upper end plate 160T and communicates with the upper compression chamber 133T of the upper cylinder 121T, is provided, and an upper valve seat (not illustrated) is formed around the upper discharge hole 190T on an outlet side of the upper discharge hole 190T.
  • an upper discharge valve accommodation concave portion 164T which extends from a position of the upper discharge hole 190T in a shape of a groove in the circumferential direction of the upper end plate 160T, is formed.
  • all of a reed valve type upper discharge valve 200T which includes a rear end portion fixed to the inside of the upper discharge valve accommodation concave portion 164T by an upper rivet 202T, and a front portion which opens and closes the upper discharge hole 190T; and an upper discharge valve cap 201T which overlaps the upper discharge valve 200T, and includes a rear end portion fixed to the inside of the upper discharge valve accommodation concave portion 164T by the upper rivet 202T, and a curved (distorted) front portion which controls an opening degree of the upper discharge valve 200T, are accommodated.
  • the lower discharge hole 190S which penetrates the lower end plate 160S and communicates with the lower compression chamber 133S of the lower cylinder 121S, is provided.
  • a lower discharge valve accommodation concave portion (not illustrated) which extends from the position of the lower discharge hole 190S in a shape of a groove in the circumferential direction of the lower end plate 160S, is formed.
  • a reed valve type lower discharge valve 200S which includes a rear end portion fixed to the inside of the lower discharge valve accommodation concave portion by a lower rivet 202S, and a front portion which opens and closes the lower discharge hole 190S; and a lower discharge valve cap 201S which overlaps the lower discharge valve 200S, and includes a rear end portion fixed to the inside of the lower discharge valve accommodation concave portion by the lower rivet 202S, and a curved (distorted) front portion which controls an opening degree of the lower discharge valve 200S, are accommodated.
  • an upper end plate cover chamber 180T is formed between the upper end plate 160T and the upper end plate cover 170T having a bulging portion which are fixed to adhere to each other. Between the lower end plate 160S and the flat plate-like lower end plate cover 170S which are fixed to adhere to each other, a lower end plate cover chamber 180S (refer to Fig. 1 ) is formed.
  • a refrigerant path hole 136 which penetrates the lower end plate 160S, the lower cylinder 121S, the intermediate partition plate 140, the upper end plate 160T, and the upper cylinder 121T, and communicates with the lower end plate cover chamber 180S and the upper end plate cover chamber 180T, is provided.
  • the upper piston 125T which is fitted to the upper eccentric portion 152T of the rotation shaft 15 revolves along the outer circumferential surface (the inner circumferential surface of the upper cylinder 121T) of the upper cylinder chamber 130T due to the rotation of the rotation shaft 15. Accordingly, the upper inlet chamber 131T suctions the refrigerant from the upper inlet pipe 105 while enlarging capacity, and the upper compression chamber 133T compresses the refrigerant while reducing the capacity.
  • the upper discharge valve 200T When the pressure of the compressed refrigerant becomes higher than the pressure of the upper end plate cover chamber 180T on the outer side of the upper discharge valve 200T, the upper discharge valve 200T is open, and the refrigerant is discharged to the upper end plate cover chamber 180T from the upper compression chamber 133T.
  • the refrigerant discharged to the upper end plate cover chamber 180T is discharged to the inside of the compressor housing 10 from an upper end plate cover discharge hole 172T (refer to Fig. 1 ) provided in the upper end plate cover 170T.
  • the lower piston 125S fitted to the lower eccentric portion 152S of the rotation shaft 15 revolves along the outer circumferential surface (the inner circumferential surface of the lower cylinder 121S) of the lower cylinder chamber 130S due to the rotation of the rotation shaft 15. Accordingly, the lower inlet chamber 131S suctions the refrigerant from the lower inlet pipe 104 while enlarging the capacity, and the lower compression chamber 133S compresses the refrigerant while reducing the capacity.
  • the lower discharge valve 200S When the pressure of the compressed refrigerant becomes higher than the pressure of the lower end plate cover chamber 180S on the outer side of the lower discharge valve 200S, the lower discharge valve 200S is open, and the refrigerant is discharged to the lower end plate cover chamber 180S from the lower compression chamber 133S.
  • the refrigerant discharged to the lower end plate cover chamber 180S is discharged to the inside of the compressor housing 10 from the upper end plate cover discharge hole 172T provided in the upper end plate cover 170T through the refrigerant path hole 136 and the upper end plate cover chamber 180T.
  • the refrigerant discharged to the inside of the compressor housing 10 is guided to the upper part of the motor 11 through a cutout (not illustrated) which is provided on the outer circumference of the stator 111, and communicates with the upper and lower parts, a void (not illustrated) of a winding portion of the stator 111, or a void 115 (refer to Fig. 1 ) between the stator 111 and the rotor 112, and is discharged from the discharge pipe 107 which serves as a discharging unit disposed in the upper portion of the compressor housing 10.
  • Fig. 4 is a plan view illustrating the intermediate partition plate 140 of the rotary compressor 1 according to the embodiment.
  • Fig. 5 is a partially perspective view illustrating a concave portion of the intermediate partition plate 140 of the rotary compressor 1 according to the embodiment.
  • a sectional arc-like concave portion 141 is provided at a position at which the upper vane 127T and the lower vane 127S slide.
  • the concave portion 141 is formed at a position which respectively opposes the end portion on the outer circumference side of the intermediate partition plate 140 in the upper vane groove 128T and the lower vane groove 128S.
  • the concave portion 141 is formed from one surface side to the other surface side in the direction of the rotation shaft 15 in the intermediate partition plate 140.
  • a width W with respect to the circumferential direction of the intermediate partition plate 140 is greater than a thickness T of the upper vane 127T and the lower vane 127S. Accordingly, as will be described later, the upper vane 127T and the lower vane 127S can enter the inside of the concave portion 141, and it becomes possible to correct inclination with respect to the sliding direction of the upper vane 127T and the lower vane 127S.
  • a depth D with respect to the radial direction of the intermediate partition plate 140 is equal to or greater than 10% of the entire length L of the upper vane 127T and the lower vane 127S.
  • D ⁇ 0.1 X L (Expression 1) is satisfied.
  • the rotation shaft 15 is bent only by an extremely small amount with respect to the shaft direction.
  • the upper piston 125T and the lower piston 125S are inclined with respect to the direction orthogonal to the rotation shaft 15 in accordance with the bending of the rotation shaft 15.
  • the upper vane 127T and the lower vane 127S are inclined with respect to the sliding direction only by an amount of clearance between the upper vane 127T and the upper vane groove 128T, and only by an amount of clearance between the lower vane 127S and the lower vane groove 128S in the upward-and-downward direction (the shaft direction of the rotation shaft 15) of the rotary compressor 1, as illustrated in Fig. 6B .
  • FIGS. 6B and 6C illustrate the inclined state of the upper vane 127T on the inside of the upper vane groove 128T in accordance with the inclination of the upper piston 125T, but the inclined state of the lower vane 127S on the inside of the lower vane groove 128S in accordance with the inclination of the lower piston 125S, is also similar.
  • the concave portion 141 is used as a positioning concave portion for fitting a positioning pin that positions the intermediate partition plate 140 with respect to a processing jig. Therefore, in the embodiment, by using the positioning concave portion as the concave portion 141 for correcting the inclination of the upper vane 127T and the lower vane 127S, it is not necessary to perform additional processing with respect to the concave portion 141 in the outer circumferential portion of the intermediate partition plate 140, and an increase in manufacturing costs of the rotary compressor 1 is suppressed.
  • the concave portion 141 is formed as a part of an outer shape of the intermediate partition plate 140. Therefore, in the concave portion 141, a cut taper for removing the intermediate partition plate 140 from the inside of a molding die when casting the intermediate partition plate 140, is provided. Specifically, the concave portion 141 is formed in a tapered shape in which the depth D with respect to the radial direction of the intermediate partition plate 140 gradually decreases from the one surface side to the other surface side in the direction of the rotation shaft 15 in the intermediate partition plate 140. Accordingly, it becomes possible to take out the intermediate partition plate 140 from the inside of the molding die during the casting.
  • the concave portion 141 is used as the concave portion 141 for correcting the inclination of the upper vane 127T and the lower vane 127S, the taper is provided. Therefore, even in a case of the depth D of the concave portion 141 at the other end of the intermediate partition plate 140, the above-described expression 1 is satisfied.
  • the concave portion 141 is provided at a position at which the upper vane 127T and the lower vane 127S slide, and at the lower dead center of the upper piston 125T and the lower piston 125S, 80% or more of the entire length in the sliding direction of the upper vane 127T and the lower vane 127S are accommodated respectively on the inside of the upper cylinder 121T and the inside of the lower cylinder 121S.
  • D ⁇ 0.1 X L (Expression 1) is satisfied.
  • the rotary compressor 1 by using the positioning concave portion for processing the intermediate partition plate 140 as the concave portion 141 for correcting the inclination of the upper vane 127T and the lower vane 127S, it is not necessary to perform additional processing with respect to the concave portion 141 in the outer circumferential portion of the intermediate partition plate 140. Therefore, it is possible to suppress an increase in manufacturing costs of the rotary compressor 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (3)

  1. Compresseur rotatif (1) comprenant :
    un boîtier de compresseur cylindrique scellé (10) placé verticalement, dans lequel une unité de décharge pour un réfrigérant est prévue dans une partie supérieure, et une unité d'entrée pour le réfrigérant est prévue dans une partie inférieure ;
    une unité de compression (12) qui est disposée dans la partie inférieure de l'intérieur du boîtier de compresseur, et qui comprime le réfrigérant aspiré par l'unité d'entrée et qui décharge le réfrigérant par l'unité de décharge ; et
    un moteur (11) qui est disposé dans la partie supérieure de l'intérieur du boîtier de compresseur, et qui entraîne l'unité de compression,
    dans lequel l'unité de compression comprend :
    des cylindres annulaires supérieur (121T) et inférieur (121S),
    une plaque d'extrémité supérieure (160T) qui ferme un côté supérieur du cylindre supérieur,
    une plaque d'extrémité inférieure (160S) qui ferme un côté inférieur du cylindre inférieur,
    une plaque de séparation intermédiaire (140) qui est disposée entre le cylindre supérieur et le cylindre inférieur, et qui ferme le côté inférieur du cylindre supérieur et le côté supérieur du cylindre inférieur,
    un arbre de rotation (15) qui est entraîné en rotation par le moteur,
    une partie excentrique supérieure (152T) et une partie excentrique inférieure (152S) qui sont prévues dans l'arbre de rotation en appliquant une différence de phase de 180° entre elles,
    un piston supérieur (125T) qui est monté sur la partie excentrique supérieure, et qui tourne le long d'une surface circonférentielle interne du cylindre supérieur, et qui forme une chambre de cylindre supérieur à l'intérieur du cylindre supérieur,
    un piston inférieur (125S) qui est monté sur la partie excentrique inférieure, et qui tourne le long d'une surface circonférentielle interne du cylindre inférieur, et qui forme une chambre de cylindre inférieur à l'intérieur du cylindre inférieur,
    une pale supérieure (127T) qui fait saillie à l'intérieur de la chambre de cylindre supérieur à partir d'une rainure de pale supérieure prévue dans le cylindre supérieur, et qui divise la chambre de cylindre supérieur en une chambre d'entrée supérieure et en une chambre de compression supérieure en venant en butée contre le piston supérieur, et
    une pale inférieure (127S) qui fait saillie à l'intérieur de la chambre de piston inférieur à partir d'une rainure de pale inférieure prévue dans le cylindre inférieur, et qui divise la chambre de cylindre inférieur en une chambre d'entrée inférieure et en une chambre de compression inférieure en venant en butée contre le piston inférieur,
    le compresseur rotatif étant caractérisé en ce que :
    une partie concave (164T) est prévue dans une position dans laquelle la pale supérieure et la pale inférieure coulissent dans la partie circonférentielle externe de la plaque de séparation intermédiaire,
    dans lequel 80 % ou plus de toute la longueur dans la direction de coulissement de la pale supérieure et de la pale inférieure sont respectivement logés à l'intérieur du cylindre supérieur et à l'intérieur du cylindre inférieur au niveau d'un point mot bas du piston supérieur et du piston inférieur,
    dans lequel, dans la partie concave, une largeur W par rapport à la direction circonférentielle de la plaque de séparation intermédiaire est supérieure à une épaisseur T de la pale supérieure et de la pale inférieure, et
    dans lequel D ≥ 0,1 x L est satisfaite lorsqu'une profondeur de la partie concave est D et que toute la longueur de la pale supérieure et de la pale inférieure est L.
  2. Compresseur rotatif selon la revendication 1,
    dans lequel la partie concave est formée à partir d'un côté de surface jusqu'à l'autre côté de surface dans la direction de l'arbre de rotation dans la plaque de séparation intermédiaire.
  3. Compresseur rotatif selon la revendication 2,
    dans lequel la partie concave est formée selon une forme progressivement rétrécie dans laquelle la profondeur D diminue progressivement du un côté de surface vers l'autre côté de surface de la plaque de séparation intermédiaire.
EP17166030.1A 2016-04-13 2017-04-11 Compresseur rotatif Active EP3232064B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016080229A JP6750286B2 (ja) 2016-04-13 2016-04-13 ロータリ圧縮機

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EP3232064A1 EP3232064A1 (fr) 2017-10-18
EP3232064B1 true EP3232064B1 (fr) 2018-09-12

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EP (1) EP3232064B1 (fr)
JP (1) JP6750286B2 (fr)
CN (1) CN107288880B (fr)
AU (1) AU2017202089B2 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6432657B1 (ja) * 2017-08-24 2018-12-05 株式会社富士通ゼネラル ロータリ圧縮機
CN110374875B (zh) * 2019-07-29 2020-11-24 珠海格力节能环保制冷技术研究中心有限公司 转子式压缩机的滑片结构、转子式压缩机及制冷设备

Family Cites Families (6)

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Publication number Priority date Publication date Assignee Title
JP2003269352A (ja) * 2002-03-18 2003-09-25 Sanyo Electric Co Ltd ロータリコンプレッサ
JP3935855B2 (ja) * 2003-03-25 2007-06-27 三洋電機株式会社 ロータリコンプレッサ
KR20060024934A (ko) * 2004-09-15 2006-03-20 삼성전자주식회사 다기통 회전압축기
WO2011030809A1 (fr) * 2009-09-11 2011-03-17 東芝キヤリア株式会社 Compresseur rotatif à multiples cylindres et dispositif de cycle de réfrigération
JP2013130061A (ja) * 2010-04-01 2013-07-04 Sanyo Electric Co Ltd ロータリコンプレッサ
CN104541060B (zh) 2012-08-09 2016-08-24 东芝开利株式会社 旋转式压缩机及制冷循环装置

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AU2017202089A1 (en) 2017-11-02
JP6750286B2 (ja) 2020-09-02
US20170298936A1 (en) 2017-10-19
EP3232064A1 (fr) 2017-10-18
JP2017190711A (ja) 2017-10-19
CN107288880A (zh) 2017-10-24
CN107288880B (zh) 2020-02-14
US10309399B2 (en) 2019-06-04
AU2017202089B2 (en) 2022-03-17

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